Jaw crushers



D. KUENEMAN 3,425,639

Feb. 4, 1969 J AW CRUSHERS Sheet Filed May 25, 1966 INVENTOR.

. DON KUENEMAN ATTORNEYS o. KUENEM-AN 3,425,639

JAW CRUSHERS Feb 4, 1969 Sheet Filed May 25, 1966 FIG 2 INVENTOR.

DON KUENEMAN, BY

Z k y r r A I RN Feb. 4, 1969 o. KUENEMAN 3,425,639

JAW CRUSHERS Filed May 25, 1966 Sheet 0f 5 DON KUENEMAN ATTORNEYS United States Patent 4 Qlaims ABSTRACT OF THE DISCLOSURE A jaw-type crusher having a plurality of individual reciprocating jaws, each operable in a crushing compartment. The individual jaws .are driven by a common drive shaft and the jaws reciprocate in an out-ofphase relationship to balance the load on the shaft.

This invention relates to crushers of the osciIlating jaw-type which are used to reduce materials, such as rocks, to .a smaller, more desirable size.

In the crushing arts, especially in hard-rock practice, little is known of the basic theory of crushing, and the development of a wide range of crushing machinery has evolved largely from empirical observation and by trial and error. In the field where coarse crushing is required probably the jaw-type crusher has the greatest degree of preeminence, and of these jaw-type crushers the doubletoggle or Blake type is probably the most common. The oval crushing movement of the single-toggle or Dalton type jaw crusher with its unique crushing action, also makes its use quite prevalent. In general, the present invention is related to the above types of jaw crushers.

Basically, the toggle-type jaw crushers have but a few, basic forms of construction, and the chief aim of the mechanical designer must be to gain greater mechanical efiiciencies in these machines, i.e., to apply the utmost crushing force with the least energy consumption by reducing friction, vibrations, inertial loading, etc.

The crushing action of these machines involves a generally reciprocating action of a jaw which causes the crushing strokes to be cyclic, power consumption to be irregular and the capacity to be directly related to the cycle time between crushing strokes. Conventional crushers of the toggle-type have but one crushing stroke for each revolution of the power shaft, and therefore the r.p.m. of the crusher is directly proportional to the capacity. In turn the rpm. of the crushers are limited generally by vibration produced by the oscillating movement of the heavy crushing jaw that prevents use of the expedient increasing the r.p.m. for greater capacity.

Capacity of conventional jaw crushers is generally increased by increasing the width of the jaw in order to provide a larger crushing feed area. When this is done, the sizes of the power shafts and bearings must be increased in size disproportionally to provide suflicient rigidity due to the greater distance between the frame support bearings and to resist the localized strains caused by twisting or racking of the jaws due to the nonuniformity of feed across the whole width of the jaw. Further, the strength of the frame and support structure must be manifestly increased to absorb the increased loading. Also, as the size of the jaw increases, the inertia of the reciprocating jaw and other moving parts generally requires that the number of crushing strokes per minute be reduced in order to avoid excessive vibration and mechanical loading, which in turn results in a somewhat reduced capacity than would be expected for the increased jaw width.

Put another way, the capacity of the machine is generally proportionate to the jaw width other things being equal, and increasing the jaw width would tend to give a proportionate increase in the capacity of the machine. However, as the width of the jaws increases the rpm. must be reduced to account for the larger inertia moments being developed, Thus, a jaw having a double width does not usually give double the capacity. In addition, as the jaw width is increased the greater strains thereon caused by twisting and racking because of the greater lever arms, require that drive and support shafts be increased substantially in diameter, i.e., nearly two and one-half times, to withstand the additional loading.

In jaw-type crushers the size reduction ratio, i.e., the size of the feed compared to the size of the product, is generally an optimum from 6:1 to 9:1, and any reduc tion which requires a greater ratio is more efliciently accomplished in a two-stage reduction. Of course, such a two-stage reduction requires the material to be handled twice, completely reduced to an intermediate size followed by a subsequent reduction, after resetting the jaws of the crusher, to the desired size.

Accordingly, it is an object of this invention to pro vide an improved jaw crusher of increased capacity without the usual accompanying increase in size and cost as is the case in conventional crushers.

Another object is the provision of a jaw crusher which has more balanced loading and increased crushing capacity for a given horsepower input.

Still another object is the provision of a jaw crusher which is capable of a simultaneous, two-stage reduction of material.

A further object is the provision of a novel multiple jaw crusher having a capacity capability of a large conventional jaw crusher wherein the inertia loading of the reciprocating jaws are dampened by one another to reduce vibration, thereby allowing higher operating speeds.

A more specific object of the present invention is the provision of a jaw-type crusher which provides a greater number of crushing strokes per minute than a conventional crusher of equal total jaw width.

Still another object is the provision of a crusher which is smaller in size and weight than the existing types of jaw crushers but having the same, or greater capacity, and which also has greater portability.

The above objects and many others which will be apparent from the specific description of this invention, can be accomplished in a jaw-type crusher wherein the crushing mechanism contains a plurality of individual reciprocating jaws which are driven by a common shaft through a plurality of eccentric cams, one for each jaw, which are equally spaced from one another on the common shaft so that the crushing stroke of each jaw is out of phase with the crushing stroke of any other jaw.

The novel jaw crusher of this invention will be better understood by reference to the specific description and the accompanying drawings wherein:

FIG. 1 is a perspective of a crusher employing the invention with parts broken away to show internal detail;

FIG. 2 is a sectional view of the crusher shown in FIG. 1 along line 22;

FIG. 3 is a sectional view of the crusher shown in FIG. 2 along line 3-3;

FIG. 4 is a sectional view of a employing the invention; and

FIGv 5 is a sectional view of the singletoggle crusher shown in FIG. 4 along line 5-5.

Referring to the drawings, FIG. 1 shows one embodiment of the novel jaw crusher 10 of this invention. The crusher is housed in an integral box-like frame 11 having two similar side plates 12, and a front plate 13 and rear plate 14, which are joined along their abutting edges, usually by welding, to form the frame. The frame also includes at least one partition plate 15 which extends between the front and rear plates dividing the frame into single-toggle jaw crusher two equal compartments. Of course, in actual practice more than one partition plate can be used, and the frame divided up into the desired number of compartments. However, the bisection of the frame into two compartments adequately illustrates the invention, and it should be appreciated that each partition plate incorporated in the frame gives it additional structural rigidity.

In each compartment formed in the frame 11, a stationary jaw 16 is tiltably suspended at its top end 17 on an upper pillar support 18 which is mounted on the inside face of the front plate. Support webs 19, which are perpendicular to the front plate and an integral part thereof, join with the pillar support to form a honeycomb-like structure for added strength and rigidity of the front plate. This strength and rigidity is necessary since the crushing loads are transmitted through the material, to the stationary jaw and then to the front plate of the frame during the crushing stroke.

For suspending it, the top of the stationary jaw 16 has a longitudinal socket groove 20 which receives the rounded end 21 of the upper support pillar in fitting engagement allowing the jaw to tilt about the joint. The bottom of the stationary jaw is supported by a lower pillar support 23 which is also incorporated into the honeycomb structure formed with the support webs 19, like the upper support pillar. This lower pillar support has a groove 24 for receiving spacers 25 which are placed between the support and the lower end of the jaw to adjust the position of the stationary jaw relative to the swing jaw for selecting the size of the crushers product. Of course, the stationary jaw could be fixed and the swing jaw adjusted relative thereto to control the product size as shown in FIG. 4 in another type of crusher.

Once the proper number of spacers 25 have been placed between the lower pillar support 23 and the bottom of the stationary jaw in each compartment, a series of clevis devices 26 connected to ears 27 on the rear face of each stationary jaw, and which have their threaded shaft ends projecting through holes in the front plate of the crusher, can be cinched down with nuts 28 hearing on washers 29 to pull the stationary plate tightly against the upper and lower support pillars. It should be appreciated that each individual stationary jaw can be separately adjusted relative to the stationary jaws in other compartments of the crusher. It is this feature which allows the crusher to simultaneously accomplish a multitude of different size reductions. For example, with the proper material handling equipment, the product from one crushing compartment can be fed directly to a second crushing compartment as feed allowing this novel jaw crusher to effect a two stage reduction simultaneously.

On each stationary jaw there is a replaceable crushing face 30, which may be equipped with teeth or ridges in a specific pattern to aid the crushing process. The teeth or ridges on the crushing faces tend to concentrate the pressure on relatively small areas, and facilitate the crushing action. Often these replaceable crushing faces are made of manganese steel, or some other hard alloy, and are retained in position in the stationary jaw by a keyway 31 at the bottom edge cooperating with the mating key-like structure at the base of the stationary jaw, and a retaining bolt 32, which, together with the keyway, holds the crushing face in the recess in the jaw. As pointed out above, each stationary jaw can be adjusted at the bottom by inserting, or removing spacers 25 when the nuts 28 on the clevis devices have been loosened. These spacer bars can be added from beneath the machine and, if desired, the bottom edge of the front plate may be relieved to provide a convenient access for installing or removing spacers.

Also mounted in each compartment near the top central portion thereof, and oriented to swing toward and away from the stationary jaw 16 in mating relationship, are swing jaws 33. Each swing jaw is swingably journalled on a common jaw support shaft 34 near the top of the crusher, which is oriented generally parallel to the front and rear plates and extends across the frame 11 between the side plates 12. The support shaft is supported at its outboard ends near the top edge of side plates by large journal boxes 35, and separate smaller support blocks 36 in each partition plate 15 dividing the frame into compartments. This arrangement allows the support shaft to be much smaller in diameter than those conventional crushers which have the same total jaw width, since the shaft is supported at its central portion in the frame as well as at the ends.

Each swing jaw 33 is somewhat arcuate in shape as can be seen in FIG. 2, and has a casting 33a at its top portion which is swingably journalled on the support shaft 34 so that the lower portion of the jaw can swing toward and away from the bottom portion of the stationary jaw 16 forming a crushing chamber or V. The arcuate configuration of the swing jaw is important to achieve greater crushing efficiency and better feed characteristics, and is more fully explained in my U.S. Patent No. 2,721, 036 issued on Oct. 18, 1955. Like its associated stationary jaw, each swing jaw has a replaceable crushing face 37 which is retained on the face of the jaw in a recess through the use of a keyway 38, cooperating structure at the bottom of the jaw and retention bolt 39 which retain the crushing face in the swing jaw.

The casting 33a at the top of the swing jaw is usually provided with lubrication means and bearings so that the support shaft 34- can be held rigidly by the journal boxes, and the swing jaws can rotate on the shaft being carried on the bearings in each casting. Near the top of each casting, and facing the feed opening of the crusher, is a feed guide plate 46 which prevents feed from overtravelling the feed opening to the rear of the machine.

While the above description covers a crusher with only two sets of jaws, it should be appreciated that more sets could be incorporated in a crusher according to this invention. Further, nothwithstanding the number of sets of jaws over one, the crusher requires that the sets operate in a maximum out of phase relationship. For example, with two sets of jaws, each crushing stroke would be 180 out of phase with that of the opposite jaw. With four sets of jaws, each crushing stroke would be out of phase with the preceding one, and four crushing strokes would occur for each revolution of the power shaft. By this arrangement, the utilization of input power is made uniform. Capacity of the crusher is also increased since the speed of the novel machine of this invention is much higher than conventional machines having an equal jaw width, because the smaller individual swing jaws have less inertia than the single large jaw found in the conventional machine and vibration is dynamically dampened.

To prevent wear on structural parts of the frame 11, wear plates 41 are fastened to the inner walls of the side plates in each compartment of the frame adjacent to the edges of the jaws, and retained thereon with bolts 42 and 43 or other suitable means. These wear plates protect the structural parts of the frame of the crusher and can be replaced when wear thereof has occurred to a degree warranting replacement.

Side plates 12 also have an outwardly projecting flange 44, reinforced with triangular stiffening plates 45, which provides the attaching means for securing the crusher in an installation. The flange is usually equipped with a plurality of holes 46 for its attachment to a suitable base.

To provide the out-of-phase relationship between the various swing jaws 33 in each compartment, each swing jaw is driven by its own eccentric cam on a common power shaft, its own set of toggles and its own pitman as can be seen in FIGS. 2 and 3. Basically, the power shaft 51 has the same number of eccentric cams 52 milled therein as there are swing jaws. Each eccentric cam is offset circumferentially on the shaft from the others depending upon the number. For example, the angular displacement between lobes in a machine having two sets of jaws would be 180. If the machine had three sets of jaws, the angular displacement between lobes would be 120, and so on.

The power shaft 51 having the same number of lobes as there are sets of jaws, is supported in the frame by roller bearings 53 in the side plates 12 at its outboard ends, and also at each partition plate 15 by a bearing 53a, so there is support between each eccentric cam. This arrangement allows the diameter of the power shaft to be much smaller than a machine having equivalent jaw Width but only a single swing jaw, since the central support of the shaft will allow it to absorb much larger distortional forces than a similarly sized shaft with a longer, unsupported span.

The eccentric cams 52 on the power shaft within each compartment usually extend almost the full width of the compartment to provide a large bearing surface for the pitman which drives the associated swing jaw. Each eccentric cam drives a vertical pitman 54 reciprocally beneath the cam, and the vertical oscillatory movement of the pitman is transmitted to a hinged journal 55 of two toggle bars, the front toggle bar 56 and the rear toggle bar 57. The hinged journal includes a shaft and mating bearing surfaces on the toggles and pitman which mate on the shaft. The two toggles in each compartment are angularly disposed between a rear support pillar 58 mounted on the inside face of the rear plate 14 with web 59, and the bottom shoe 60 of each swing jaw 33 when each swing jaw is in the jaw-open position, and return springs 61 beneath the toggle bars bearing against the hinged journal urging them up into a Vd relationship. These springs also urge upward the pitman 54 mounted on the journal between the front and rear toggles, against the associated eccentric cam 52 on power shaft 51.

As the power shaft turns and eccentric cam forces the pitman downwardly, the Vd toggles 56 and 57 are straightened and, as this occurs, the swing jaw is pushed toward the stationary jaw on a powerful crushing stroke. It is through this arrangement that a tremendous mechanical advantage is developed and powerful crushing action is generated between the stationary and swing jaws in each compartment. Since the loads on the toggles are largely compressive loads, the toggle bars are able to handle tremendous loads.

In order to facilitate the return of the swing jaw 33 after its crushing stroke, a tie rod 62 is connected to an car 63 on the base of the shoe 60. This tie rod in turn is connected through a return spring 64 to frame 11 through support 65a via base plate 65, so that the movement of the jaw toward the stationary jaw on the crush ing stroke will compress the spring and the energy in the compressed spring will aid in pulling the swing jaw back, as the toggle bars V, for a subsequent crushing stroke.

In the preferredembodiment of the invention shown in FIGS. 1, 2 and 3, the pitman 54 is not capped on the eccentric cam 52 in each compartment. This design reduces the weight of the pitman, and also the inertia forces that would be developed by the heavier weight capped pitman. While such a design is not possible in conventional crushers, it is possible in the structures of this invention since the drive assemblies are enclosed with a sub-compartment within each compartment of the frame, and closed by a cover 66 and base plate 65. Near the bottom of the sub-compartment at its front end there is an aperture which is closed by a flexible diaphragm 67 which is connected therebetween and the bottom of shoe 60 of each swing jaw around the joint of toggle 56 therewith. Thorugh the use of this flexible diaphragm and the enclosed sub-compartments all dust, dirt and the like are kept out of the sub-compartments, and these materials cannot get into the open eccentric bearings, as would be the case if no closed sub-compartment was provided. Further, this sub-compartment acts as a lubricating oil sump, and allows the hearings in the compartment to be sprayed continuously with lubricating oil during operation of the crusher.

This lubrication is usually accomplished through the spray pipe 68 which receives pressurized oil from pump 69 that is driven at one end of the power shaft 51 through a small sub shaft 69a. The oil collected from the sump in each driving assembly sub'compartment via sump line '70 passes through filter 71, which assures that the oil will be free of foreign, solid particles when sprayed on to the moving parts within each compartment. This arrangement allows for continuous recirculation of lubricating oil, and provides a certain degree of cooling of the bearings surfaces operating within each sub-compartment. The spray pipe may be equipped with valves 68a to adjust the oil flow of the various compartments so that it can be regulated for the desired rate. Also, the individual components can be provided with oil grooves and slots in the shaft and bearing surfaces through which the oil may be carried to the internal faces of the bearmgs.

At the end of the power shaft 51 opposite pump 69, a combination flywheel and pulley 72 is attached to the power shaft. The hub 72a of the flywheel is not fixedly connected to the power shaft, since tra-mp iron and the like getting into the jaws could induce strains which would cause structural damage to the machine if there were not provisions for preventing the inertia of the flywheel and driving force of the motor from causing structural failure. More conventional machines use toggles which contain shear sections so they will separate and relieve the force on the swing jaw in the event of a tramp iron jam-up of the machine. However, in the instant invention, this problem is eliminated by connecting the flywheel to the power shaft through a spring leaf 73 which is received in a detent 74 along the inside periphery of the flywheel.

The resiliency in the leaf will cause it to pop outboard,

beyond the outside periphery of the flywheel if it is forced out of its detent.

Through the above arrangement, when tramp iron jams any of the jaws in the crusher the spring leaf will be forced out of its detent and will snap out-board of the rim of the flywheel which will allow the flywheel to freewheel on the power shaft without interference. This feature allows the power shaft to stop immediately before structural damage has occurred when jam-up occurs in any of the swing jaws. Subsequently, the tramp iron can be removed and the flywheel braked to a stop. Thereafter, the spring leaf may be pressed inboard of the rim of the flywheel so that it will again be received in the detent for connecting the power shaft to the flywheel and pulley. This safety device for jaw crushers is more fully described in my US. Patent No, 2,915,157 issued on Dec. 1, 1959.

An alternate embodiment of the invention is shown in FIGS. 4 and 5 where it is incorporated into a singletoggle or Dalton type crusher 110. The box-like frame 111 has stiffening stringers 112 incorporated in its front plate 113 and rear plate 114, as well as its side plates 115. These assure additional rigidity of the frame. A central partition 116 divides the box-like frame structure into two compartments.

In each compartment a stationary jaw 117 is mounted using semi-permanent spacers 118 to position the jaw. The power shaft 119 is carried centrally, adjacent to the top edge of the side plates of the crusher, in bearing boxes 120, and at each end thereof, and is also supported by a smaller bearing box 121 in the central partition with all the bearing boxes containing roller bearing 122.

The power shaft is very much like that described in the first embodiment of this invention, and has two eccentric cams 123 which are positioned on the shaft to obtain the maximum out-of-phase relationship between the crushing strokes of several sets of jaws. However, in this crusher, the upper portion of swing jaws 124 is carried directly on the eccentric cam through large journals 125 rather than on a separate support shaft. The lower end of each jaw is supported by a single toggle bar 126 between its shoe 127 and an adjustable block 128 which is supported on the rear plate through wedging block 129, as can be seen in FIG. 4. By means of this arrangement, the spacing of the lower ends of each stationary jaw and its swing jaw carried on the power shaft can be adjusted for the desired product size. A tie rod 130 is connected to an ear 131 on the bottom of the shoe of each swing jaw, and compresses a spring 132 between its end and the rear plate when the swing jaw begins its crushing stroke. The force stored in the compressed spring pulls the jaw back, as the jaw cycles, for a subsequent crushing stroke.

In operation, the stroke of this single-toggle crusher is somewhat different from the double-toggle type described before, and it has two flywheels 133, one on each side to help even out the cyclic loading. One can be used as a pulley and as these flywheels are rotated, each swing jaw 124 carried by its associated eccentric cam 123, and toggle bar 126, make an oval-type crushing movement toward and away from its associated stationary jaw 117.

As in the crusher previously described, the crushing faces are removable, and crushing face 134 is held in a recess in the face of the swing jaw by a groove and tie bolt 135.

In the single-toggle crushing machine the out-of-phase relationship of the swing jaws reduces the energy necessary to lift these jaws since a dynamic balance of the weight of the several jaws is achieved when one jaw is going up, and the other is going down. Further, the outof-phase relationship dampens the vibration of the machine, thereby improving efficiency, and reducing power consumption. It also allows the machine to run at higher speeds. The flywheel may be connected to the power shaft by the release mechanism described previously.

Utilizing either of the two designs described above the product opening between the several sets of jaws can be adjusted to different gaps, and the rock reduced by one set of jaws may be fed directly to another set for a second-stage reduction, and so on. In practice, the invention requires at least two crushing chambers, or compartments, as described above. However, it is not limited to two. Further, it should be appreciated that the number of swing jaws which can be incorporated into a crusher in this manner is limited mainly by the torque loads on the power shaft since the support shaft for the swing jaws could always remain the same diameter for the same size swing jaws no matter how many are employed.

Not only does this novel machine provide improved efiiciency, but it affords the operator a much greater flexibility, such as a two-stage reduction mentioned above. In addition, the size and weight of a crusher according to this invention is substantially less than a conventional machine of equivalent capacity. For example, using the invention described herein, the size of the machine of equivalent capacity would weigh about only half of that of a conventional machine with the same rated capacity.

I claim:

1. An improved jaw crusher capable of high speed operation comprising:

(a) a main box-like compartments;

(b) a stationary crushing jaw mounted in each crushing compartment;

(c) a swing jaw swingably mounted in each compartment for reciprocal movement toward and away frame having at least two crushing 8 from said associated stationary jaw in each compartment to define a plurality of crushing zones;

(d) a common drive shaft and flywheel including one eccentric cam thereon for each swing jaw, each eccentric cam for each jaw circumferentially spaced equally about the shaft from other eccentric cams so that the reciprocal movement of each of said swing jaws is in an out-of-phase relationship with the movement of any other swing jaw; and

(e) connecting means between each swing jaw and its associated cam which includes a bearing journal in the top of each swing jaw carried on its associated cam and a toggle bar means supporting the bottom of each swing jaw whereby an oval crushing movement is circumscribed by each swing jaw.

2. An improved jaw crusher capable of high speed operation comprising:

(a) a main box-like frame having at least two crushing compartments;

(b) a stationary crushing jaw mounted in each crushing compartment;

(c) a swing jaw swingably mounted in each compartment for reciprocal movement toward and away from said associated stationary jaw in each compartment to define a plurality of crushing zones;

(d) a common drive shaft and flywheel including one eccentric cam thereon for each swing jaw, each eccentric cam for each jaw circumferentially spaced equally about the shaft from other eccentric cams so that the reciprocal movement of each of said swing jaws is in an out-of-phase relationship with the movement of any other swing jaw; and

(e) connecting means between each swing jaw and its associated cam which includes a common bearing shaft swingably supporting each swing jaw, a pitman cooperating with each cam and a pair of hinged toggle bars associated with each pitman positioned between the frame and the bottom of each swing jaw which are reciprocated across their hinge joint by said pitman to effect a reciprocation of the associated swing jaw.

3. The improved jaw crusher as defined in claim 2 wherein the pitman and toggle bars driving each swing jaw are enclosed in a sub-compartment into which oil is sprayed for lubrication by a pump driven by the common power shaft.

4. The improved jaw crusher as defined in claim 3 wherein the pitmans are not capped on their eccentric cams and are urged thereagainst by resilient means in order to lessen the inertia of the pitman.

References Cited UNITED STATES PATENTS 864,573 8/1907 Sturtevant 24l148 873,080 12/1907 Philips 241-268 X 2,721,036 10/1955 Kueneman et al 241269 2,784,916 3/1957 Traylor 241-268 2,915,157 12/1959 Kueneman et a1 19256 ANDREW R. JUHASZ, Primary Examiner.

U.S. C1. X.R. 24l217 

